Ratio control for transmission mechanism



H. J. KIRSCHNER ET AL 2,057,151

RATIO CONTROL FOR TRANSMISSION MECHANISM Filed April 26, 1935 4 SheetsSheet l 3, 1936- H. J. KIRSCHNER ET AL 1 RAT IO CONTROL FOR TRANSMISSION MECHANISM Filed April 26, 1935 4 Sheets-Sheet 2 Oct. 13, 1936. I H J KlRscHNER ET AL 2,057,151

RATIO CONTROL FOR TRANSMISSION MECHANISM Filed April 26, 1935 4 Sheets-Sheet 3 Oct. 13, 1936- H. J. KIRSCHNER ET AL 2,057,151

RATIO CONTROL FOR TRANSMISSION MECHANISM Filed April 26, 1935 4 Sheets-Sheet 4 Gum/M436 Patented Oct. 13, 1936 UNITED STATES.

PATENT ()FFICE RATIO CONTROL FOR TRANSMISSION MECHANISM Delaware Application April 26, 1935, Serial No. 18,426

15 Claims.

Thisinvention relates to mechanism for controlling and varying the ratio of a variable speed power transmission mechanism. It is designed particularly for use in variable speed power transmission mechanisms of race and roller type.

It has already been proposed to control the ratio of variable speed power transmission mechanisms through the influence of the muscular efforts of the operator and the movements of a device responsive to the velocity of some part of the power train.

It is an object of this invention to simplify and improve the operation of control mechanisms of this type.

The invention comprises a ratio changing device, a governor, shown as adapted to be driven by a power output element of the transmission, operating in response to increasing speed to move the ratio changing device.so as to shift up", or tilt the rollers into a higher ratio position, and means responsive to operator control tending by elastic force to move the ratio changing device so as to shift down or tilt the rollers into a lower ratio position. Both governor and operator control are applied to the ratio changing device through the intermediary of a difierential lever. An important feature of the invention is embraced in a spring connection between the diiierential lever and an operator controlled lever linked thereto, said spring fulfilling the functions both of a power spring operating to shift down to lower ratio when released by the operator's control and of a lash take-up to obviate the ill effects of loose connections, The spring and associated parts as described are so disposed as not to increase the required shift efforts of the governor; and by taking up the lash, tendency of the rollers to hunt during ratio changing is avoided, and incidentally there is obviated the necessity of placing fine tolerances on the fit of pin and hole connections. A dashpot is arranged to retard too rapid shifting movements made by the operator. Means are also present to cushion movements of extreme governor speed when the rollers have reached the limit of tilt to high ratio positions, and the tension of the power spring described is utilized for this purpose.

In the accompanying drawings, in which like reference characters indicate like parts throughout the several viewsr Fig. 1 is a view, partly in side elevation and partly in section, of a transmission casing broken away and exposing the transmission-connected end of a ratio control mechanism adapted to adjust and regulate the ratio position of the rollers of a race and roller transmission mechanism, and of an output speed-responsive governor adapted to influence said mechanism;

Fig. 1a is a diagrammatic illustration of the operator-actuated end of said control mechanism and its connections to the engine throttle;

Fig 1b is a view of the mechanism illustrated in Fig. 1a but with the parts shown in different phase relations;

Fig. 2 is a view of certain parts of the control mechanism as seen from above with cover plate removed from the inclosing casing;

Fig. 3 is a section in a plane indicated by line 3-3 of Fig. l;

Fig. 4 is a section in a plane indicated by line 4-4 of Fig. 2;

Fig. 5 is a section through a dashpot used to prevent too rapid movement in changing ratio by the operator, and

Fig. 6 is a detail plan, showing an operator con trolled lever and associated parts external of the casing.

The drawings illustrate a ratio changing arm secured to a ratio changing shaft and the control mechanism operative thereon, the major portion of which is disposed within the rear of the casing of a race and roller transmission mechanism. The ratio control mechanism is responsive to a governor within the casing rotated by the output end of the transmission, and also to the muscular efiorts of an operator, exerted upon an accelerator pedal or equivalent, and transmitted to the control-mechanism by link and lever connections, outside of the casing. They show also the connections of the accelerator pedal to the throttle and the varying relations assumed by throttle and ratio controlling means.

The transmission casing is indicatedby numeral l0. Casing it) has an opening through the upper wall, closed by a removable cover plate 12, and an opening through the rear wall closed by a removable cover plate l4. Access may be had to the inclosed parts through these openings. Cover plate 52 is also equipped with a supporting bearing for an operator controllable primary lever constituting an element of the control mechanism.

One of the driven races of the transmission mechanism is shown at l6, and one of the intermediate adjustable transmission rollers at l8. The transmission output shaft is indicated by numeral 20. The remaining races and rollers, power input devices and final power output elements are not shown, as they are not essential to an understanding of this invention. Inclosure ,race I6 and overhangs toward the rear.

cylinder v22 adjustably secured to shaft 20, by means not shown, is equipped with a collar, 24, rigid with the cylinder, which presses against the inner edge of annular plate spring 26; the

outer edge of spring 26 bears against the back of race I6 at 21. Cylinder 22 is normally adjusted axially so as to stress the spring 28 to apply a precalculated elastic pressure to the races and rollers. Within the cylinder 22 are torque loading devices (not shown) for loading the races and rollers in order to increase the traction between them in proportion to increase of load. The torque loading devices and adjusting means referred to are not material to this invention and are fully disclosed in application Serial No. 728,624, filed May 31, 1935, Patent No. 2,030,203 dated February 11, 1936.

The ratio control mechanism ofthis invention is under the joint influence of the operator, exerted through the usual accelerator pedal or equivalent, and of a governor responsive to the speed of rotation of some part of the transmission train between prime mover and final 'power take-off, in accordance with the principles and modes of operation disclosed in application Serial No. 521,324, filed March 9, 1931, and application Serial No. 598,350, filed March 12, 1932. In this embodiment the governor is rotated by one of the power output races I6.

The governor utilized is of a type that is the subject of application Serial No. 712,308, filed February 21, 1934, Patent No. 2,003,817, dated June 4, 1935, and is illustrated sufliciently for the purposes of this invention in Figs. 1 and 3. An annulus or rim member 28 is shown secured to The outer edge of a flat annular spring 30 is secured to the inner periphery of rim 28 by any suitable means that will hold said outer edge from axial movement, but allow the inner edge to yield to axially applied forces. In Fig. 1 spring 30 is shown confined between the edge 32 of a flanged ring 34, welded or otherwise fixed to the back of race I6, and lugs 36 struck-up from rim 28. Fly weights 38 are hooked over the inner edge of spring 30' by means of lugs 40 spaced from the arm 44, and thereby sleeve 50, to move rearward. .The spring opposes centrifugal force of the revolving weights and restores the sleeve to the initial position shown in Fig. 1 as soon as the centrifugal pull upon the fly weights becomes less than the elastic force of the spring.

Spring 30 is shown composed of two annular spring layers 30' and 30". Spring layer 30' should be elastically stressed with a bias toward the race I6 in the position shown, thus tending always to oppose the action of centrifugal force on the fly weights 38. Spring layer should be elastically stressed when in the position illustrated with'a bias away from race I6 during the initial range of movement of the two layers under the pull of the fly weights, but thereafter, when its normal position of zero stress has been passed, adding its elastic force to that of spring layer 30' to oppose the centrifugal force exerted by the fly weights. The springs may be said to be differentially stressed in order to impart to them a characteristic that permits a low spring resistance and considerable amplitude of movement of the governor arms 44 during relatively low output speed and thereafter applies a greater resistance and a lower ratio of governor arm movement to output speed.

The governor influences the ratio control mechanism through the sleeve 50 andassociated mechanisms. Sleeve 50 is provided with a cylindrical ball socket at 52 engaged by a ball 54 on a crank pin secured to the end of crank arm 56. Crank arm 56 is secured to the lower end of a rock shaft 58. The latter is rotatably fitted in a long bearing member 60 shown as secured to a shelf-like supporting bracket 62 preferably formed integral with casing I0. The shelf-like bracket 62 is drilled to receive both the bearing member 60 and also a pivot pin 64, as illustrated best in Fig. 3. Bearing member 80 is formed with a head 86 from which projects at right angles a fiat arm 68. When the bearing member 60 is properly seated in the hole provided for'it in bracket 62, the head 66 and arm 88 lie snugly against the upper face of said bracket, and a smaller hole in the end of the arm registers with a corresponding hole in the bracket so that pin 64, passing through both arm and supporting bracket prevents the former from moving and thus prevents rotation of the bearing member 80. Bearing member 60 is also clamped to bracket 62 by nut 10 and lock washer I2. Secured to the upper end of shaft 58 is an arm 14, supporting a pin I6 on which a balanced or differential lever I8 is fulcrumed, as clearly shown in Fig. 2. The end 80 of one arm of lever I8 is universally jointed to a link 82, the other end of said link being connected by a ball joint 84 to one arm 86 of a two-armed rock lever sleeved on control shaft 88, as best shown in Fig. 3. This arm 86 will be designated the ratio changing arm or device. The other arm 80 of said twoarmed rock lever is, in the embodiment illustrated, connected to a member 92 which actuates the control element of a servo motor mechanism 94 of any suitable type, such, for example, as is disclosed fully in application Serial No. 4,220, filed January 31, 1935.

The servo motor, when energized, rocks arm 86, which is secured to shaft 88. Shaft 88 in turning moves arm 98 to which is secured one end of a link I00. Link I00 is connected by intermediate devices, not, shown, to the rollers I8 in order to adjust them to different ratio positions.

As this invention is concerned only with the control mechanism on the control-input side of the servo mechanism and ratio changing arm 88, the particular construction of the servo mechanism and of the output control mechanism between control shaft 88, arm 88 and rollers I8, are not shown in detail. They form the subject matter of separate patent applications.

Thus far the means by which a governor is linked with the ratio control arm to impress upon it an influence responsive to speed has been -:described. The means bywhich the accelerator lever under the operators-management is contransmission ratio are applied to the end IIlI of the long power arm of a primary lever I02 disposed outside of casing I0 and fulcrumed on cover plate I2 by means of fulcrum shaft I06 to which lever I02 is keyed as shown in Fig. 3. Shaft I04 has bearing in a hole drilled through a thickened area of the cover plate I2 at boss I06. An extension arm I00 of lever I02 is connected by a strong pull spring IIO to a fixed inchorage lug II2 rising from an attachment II4 bolted to cover plate I2. A stop screw I I6 adjustable in lug II8, also rising from attachment II4, acts to limit the extent of movement of arm I08 and lever I02 in the direction of the elastic force exerted by spring I I0, that is, counterclockwise as viewed in Fig. 1. A lever work-arm I20 is fixed to the lower end of shaft I04 within casing I0, and a crank pin I22 extending downward is fixed to the end of said arm I20. Lever I02 may be moved clockwise (as viewed in Fig. 1) by an effort of the operator, exerted upon the ac celerator pedal or equivalent device, which effort is communicated to the lever through means including a link I 24 connected to the end I-0I of said lever. A tendency to move counterclockwise is imparted to said lever I02 by spring H0. The mechanism by which the muscular effort of the operator may be transmitted to link I 24 and lever I02 will be described hereinafter.

Pin 64, the axisof which is in line with the axis of lever shaft I04, and which has been previously mentioned as passing through arm 66 of bearing sleeve 60 and through shelf-like bracket 62 in order to prevent arm 68 and bearing sleeve 60 from rotating, also functions as a pivot on which a secondary lever I26 is fulcrumed. Pin 64 has a head 65 adapted to confine lever I26 between it and bearing-sleeve arm 68. The lower half of said pin is reduced in diameter, the reduced part extending through said arm 66 and bracket 62, the shoulder formed at the junction between the pivotal bearing part about which the lever rocks and said reduced part resting on said arm 68. The end of the reduced part is threaded for reception of a lock washer and nut 61 to secure pin 64 firmly to bracket 62.

Lever I26 consists of a relatively long arm having a slotted or forked end 26 embracing one end, preferably a spherical terminal I26, of one element I30 of a yieldable resistor to be presentlydescribed, and a shorter arm I32, pivoted at I36 to one end of a link I36 the other end of which is connected by a lost motion pivotal joint to arm I40 of said previously mentioned differential lever 18 fulcrumed at 16 on governor moved arm. 14. The lost motion joint consists of a pin E36 fixed to arm I40 entering a slot I36 in link I36. At the end of short arm I32 of lever I26, further from the fulcrum than link-connecting pin I35, one end of a tensioned Spring I42 is attached, as by a pin I44, the other end of said spring being attached to arm I40 of lever 16, at a point I46, adjacent the connection of link I36 thereto at pivot I38. Upon inspection of Figs. 1 and 2, it will be perceived that said spring I42 not only takes up all backlash and looseness but also acts as a power spring tending to move lever I26 clockwise and press the long arm thereof against pin I22 of arm I20 of the operator controlled lever I02; and that said spring also tends in shortening to rock lever 16 counterclockwise, due to the greater mechanical advantage exerted through arm I32 on the right-hand end of link I36 than on the left-hand end of link I36 through arm I40, and therefore to rotate ratio control arm 66 counterclockwise as viewed in Fig. 3, which adjusts the ratio into low. The elastic force of spring I62, it is to be noted, is less than that of spring H6 connectedto lever I02.

The resistor connected with lever I26 is illustrated in Fig. 5. It consists of a double acting dashpot comprising a liquid tight casing having opposed cylinders I50 and a chamber I52 above and communicating with the cylinders midway between them. The upper part of chamber I52 is somewhat expanded to receive a packing bellows and is closed by a cap piece I54 having a central lever receiving opening I56 and depending spaced lugs I58, between which lever I30, previously referred to as an element of a resistor, is fulcrumed on a pin I60. A packing bellows I62, clamped to the casing by cap piece I54 and sealed to the lever I30 just below collar I64 thereon, renders fluid-tight the opening throughwhich lever I30 enters the casing. Within the cylinders are fitted pistons I66 integrally or otherwise rigidly connected by an intermediate body I68 having a cylindrical opening I10 merging upward into a conoidal throat I12. A spherical terminal I14 of lever I30 operates within cylindrical opening I10 of the intermediate piston body. Between the pistons I66 and cylinders I50 ventways are provided in any suitable manner to permit passage of liquid past the piston. In the construction illustrated the fit of the pistons is loose enough to allow seepage of fluid between them and the cylinder wall when said pistons are moved in either direction. Chamber I52and the cylinders are designed to contain any oily liquid suitable for dashpcts. The dashpot casing may be supported within the transmission casing I0 by brackets I16 to which the dashpot casing may be secured by bolts passing through lateral lugs I18 on said dashpot easing into the brackets I16, which are fast to the transmission casing. The dashpot, it will be perceived, tends to retard movement of the lever I26 by opposing substantially equal resistance to movement of the lever in either sense of swing.

An operator's will may be impressed upon the transmission to adjust the ratio and simultaneously upon the prime mover which drives the transmission by means to be now described. It has previously been explained that the operators control effort upon the transmission ratio changing mechanism is exerted upon lever I 02 through a connection of link I24 to an accelerator pedal or equivalent member. Figs. 1a. and 1b show one mechanism for connecting an accelerator pedal I60 to link I24 and to the engine throttle. A cam plate I02 is pivoted to move angularly about a fixed axis I84. Accelerator pedal I60 is shown linked to a projection or arm I66 on the cam plate by rod I90. Cam plate I62 possesses two active cam surfaces I92 and I94. Cam surface 592 is illustrated as formed upon one edge (the upper) of the cam plate and as composed of a delay surface I96 concentric with the axis I64 and a non-concentric activating surface I96. Cam surface I94 is formed as one side of a slot. Cam surface I94 also has a delay or inactive surface 200 concentric with the axis of the cam plate E62 and a non-concentric activating surface 202.

Link I24 is pivoted to the end 204 of the work arm of a lever 206 movable about a fixed fulcrum pin 206. The end of the power arm of lever 206 bears upon cam surface I92, preferably, by means of a roller 2I0. Roller 2I0 is elastically urged into contact with cam surface I02 by the spring IIO, which tends to swing lever I02 counter-clockwise pulling link I24 toward the right as viewed in Figs. 1, 1a, and lb, and rocking lever 200 counter-clockwise, thus maintaining roller H0 in contact with cam surface I02. Depression of accelerator pedal I 00 has no effect on lever 200 during the initial portion of the depressing movement because of the contact of roller 2I0 at that time with the delay surface I90 of the cam. During continued depression of the accelerator pedal, when the activating surface I00 comes into contact with roller 2I0, lever 200 is rocked clockwise as viewed in Figs. la. and 1b, pulling link I24 leftward, rocking lever I02 clockwise against the resistance of spring II 0, and causing pin I 22 of arm I20 to free lever I20 so that said pin does not prevent clockwise movement of lever I20.

A throttle of ordinary butterfly valve type is diagrammatically indicated at 2I2. It is rotatable by force applied to an attached arm 2I4 and is biased preferably toward closed or engine idling position by a spring. A two-armed lever pivoted to a fixed fulcrum pin at2I0 has a relatively short power arm 220 provided preferably with a terminal roller 222 bearing against the cam surface I04 of the cam slot in cam plate I02. The relatively longer work arm 224 of said lever fulcrumed at H8 is tied by a link rod 220 to the throttle arm 2I4. The early portion of the depression movement of accelerator pedal I00 causes the active cam surface 202 to rock lever 220, 224, thus opening the throttle 2I2. After camplate I02 has been moved by accelerator I00 to a degree that brings delay cam surface 200 into engagement with roller 222 on power arm 220 of lever fulcrumed at 2I0, further depression of accelerator pedal I80, has no effect upon the throttle, but does move lever 200 clockwise pulling link I24 leftward and rocking lever I02 clockwise.

The drawings, Figs. 1, la, 2, and 3 show the power transmitting elements in low ratio relation, the engine throttle closed, the accelerator pedal fully released, and all other parts of the ratio control mechanism in corresponding low ratio position.

Assuming the engine to have been started and the transmission train coupled to it, the accelerator pedal I00 is depressed as is usual in starting or accelerating motor vehicles. Depression of the accelerator pedal rotates cam plate I02 clockwise and moves the throttleioward fully open position. Assuming pedal I 00 to have been moved from position I, as indicated on the diagram Fig. la, to position II, arm I00, fixed to cam plate I02; will have been'rotated to corresponding position II; arm 224 and throttle-valve arm 2I4 will also have been moved to position II in their respective arcs of movement. The governor will have shifted ratio changing arm 00 to a higher ratio position by swinging arm I4 clockwise (Fig. 3) and thus moving said arm 00 toward high ratio positiom The car may be assumed now to be traveling at av rate of 50 to 60 miles per hour, the speed of the car during the range of accelerator movement from position I to position II, having been controlled by the combined effect of throttle opening and governor control of the ratio changing arm 00. The effort of the operator on the accelerator pedal has had no effect upon the .mnositionnthedelaymrfacelfiolcamlll .has been in contact with roller 2| 0 on lever 200 so that lever 200 has imparted no movement to link I24 and arm I02, which transmits the operator's muscular effort to the control mechanism.

If.pedal I00 be moved to position III, (Fig. 1b) cam-plate arm I00 will be moved to corresponding position III and this movement of the cam plate will swing arm 224 to position III on its arc of movement, which will in turn move the throttle valve arm 2I4 to corresponding position III. 'Position III of the throttle is shown as the wide open position. At this position roller 222 on lever arm 220 is at the turn or corner of thecam slot or cam surface I94. Any furtherswing of the cam plate clockwise can impart no movement to the throttle because the delay surface 200 then contacts with said roller 222 The movement of pedal I 00 from position II to position III has moved the lower end 204 of lever 200 to corresponding position III on its arc of movement. The engine has now accelerated and the governor has tended to move the arm I4 further clockwise. But the movement of arm 200 to position III has pulled the link I24 and swung lever I02 clockwise, thus removing pin I22 rightward (Figs. 1 and 2) away from lever I20. Spring I42 now contracts, pulling lever I20 clockwise against dashpot resistance and impart- .ing a differential movement to lever arms I32 and I40 the result of which is a counter-clockwise movement of the differential lever I0 and a forcing of ratio control arm 00 toward a lower speed ratio, position. This change of ratio affording higher mechanical advantage with wider throttle opening allows the engine to attain a higher velocity, while the transmission ratio is now under operator control.

If now the accelerator be pressed down to position IV (Fig. 1b), cam-plate attached arm I00 moves to corresponding position IV. As delay surface 200 now contacts with roller 222 on arm 220, arm 224 can move no further leftward (Fig. 1b) and throttle position does not change; but the lower end 204 of lever arm 200 moves leftward to position IV on its arc of movement and pulls link I24 leftward and lever I02 clockwise, thus removing pin I22 still further rightward (Fig. 2) and allowing spring I42 to pull lever I20 clockwise against dashpot resistance until it again bears against pin I 22, and the differential movement of arms I 32 and I40 again results in a counterclockwise movement of differential lever "I0, and a tendency to move ratio control arm 00 again toward low ratio position. Thus with reduced ratio the engine may speed .up to its peak efficiency. And when that peak movement of arms 00 and 00. Should the governor attain a speed under any condition of car driving sufficient to tend to ,cause tilting of the rollers to the limit of high ratio position, the differential lever 10 may then fulcrum on its end joint 00. allowing pin I30 in the end of arm I40 to move around pin 10 leftward (Fig. 2) in the slot in link I20, resisted by spring I42.

If pressure on pedal I00 is relaxed so that it rises and enters the range between positions II and III, the throttle partially closes and spring (not shown) are provided to limit the angular H moves lever I02 counter-clockwise, moving pin I22 leftward (Figs. 1 and 2) against dashpot resistance thereby rocking differential lever'l'd clockwise, and so tending to shift to a higher gear ratio. Thus reducing the fuel supply of the engine and increasing the load upon it by introducing a higher gear ratio tends to slow the car speed. Further relaxation of pressure on' pedal I80 reduces still more the fuel supply and permits spring H0 acting on lever I02 to press lever I26 further in a counter-clockwise sense thus tending still further to maintain a high transmission ratio, and so slowing down the en? gine and vehicle speed. When pedal I80 is between positions I and II the governor influences ratio in cooperation with the operators eifort. The governor tends during diminishing vehicle speed to lower ratio while the effort of spring Ill] (regulated by the operator) tends to raise the ratio. When the vehicle comes to a stop the governor has assumed the position shown in the drawings and has adjusted the rollers to low ratio position, suitable to allow the car to be started again.

We claim:

1. In a variable speed transmission mechanism of the kind described, a ratio changing device, a speed responsive governor, a differential member movable by the governor, means for connecting the differential member to the ratio changing device, an operator-controllable device, a mechanical connection between said differential member and said operator-controllable device, and a spring connected to said differential member and said operator controllable device tending to shorten the distance between said member and device at the points of connection of said spring.

2. In a variable speed transmission mechanism of the kind described, a ratio changing device, a differential lever, a governor influenced element pivoted to said differential lever between the ends of the latter, a connection from one arm of said differential lever to said ratio changing device, a pivoted operator-controllable arm linkconnected to the other'arm of said differential lever, and a take-up and power spring connected to said link-connected arms at points which enable the spring to operate with a greater mechanical advantage on one arm than on the other.

3. In a variable speed transmission mechanism, a combination as defined in claim 2 wherein the take-up and power spring is connected to said link-connected arms at points which enable the spring to operate with greater mechani. cal advantage on the mierater-controllable arm than on the differential lever.

4. In a variable speed transmission mechanism, a combination as defined in claim 2 in which the take-up and power spring is connected to the differential lever between the link connection thereto and the pivotal connection thereof to the governor influenced element, and to the operatorcontrollable arm at a greater distance from the fulcrum of the latter than the link connection.

5. In a variable speed transmission mechanism of the kind described, a ratio changing device, a differential bell crank lever, a governor operated member to which said bell crank member is pivoted at the angle of the latter, a mechanical connection between the ratio changing device and one arm of said differential lever, an operatorcontrollable arm, a link connecting said operator controllable arm to the other arm of said differential' lever, and a spring having its ends joined to said link-connected arms at points that enable the spring to operate with a greater mechanical advantage on one arm than on the other.

6. In a variable speed transmission mechanism of the kind described, a ratio changing device, a differential bell crank member, a governor-operated member to which said difierential member is pivoted between its ends, means for mechanically connecting one arm of said diiferential member to said ratio changing device, said governor-operated member being constrained to move its pivotal connection with the differential member toward and away from said ratio changing device and operator-controllable means including a spring arranged to apply its elastic force to the other arm of said differential member in a direction substantially at right angles to the direction of the force applied thereto by the governor-operated member.

'7. In a variable speed transmission mechanism of the kind described, a ratio changing device, a diiferential lever connected thereto, a movable member to which said differential lever is pivoted between its ends, a governor for operating said movable member and thereby changing the position of the pivotal connection between said differential lever and said movable member, and operator-controllable means including a spring exerting its tension to rock said differential lever on said pivotal connection.

8. In a variable speed transmission mechanism of the kind described, a ratio changing device, a speed responsive governor, a differential member, means for transmitting movement from the governor to the differential member, means for connecting the differential member to said ratio changing device, operator-controllable means including a primary lever, and a secondary lever, said primary lever having means arranged to contact with the secondary lever in one sense of movement only, a spring tending to move said primary lever in the sense of direction which causes it to engage with the secondary lever, a link connecting one arm of the secondary lever with said differential member, a take-up and power spring connected to said differential member and to said arm of said secondary lever, the elastic force of said take-up and power spring being inferior to that of the spring acting on said primary lever.

9. In a variable speed transmission mechanism of the kind described, a ratio changing device, a speed responsive governor, a differential member, means for transmitting movement from the governor to the differential member, means for connecting the diiferential member to said ratio changing device, operator controllable means including a lever, a link connecting one arm of said lever with the differential member, a take-up and power spring connected to said differential mem.

ber and to the link connected arm of said lever.

10. In a variable speed transmission mechanism of the kind described, a ratio changing device, a speed responsive governor, a differential lever, means connected to said differential lever between its ends for transmitting movement thereto from the governor, means for connecting one arm of said differential member to said ratio changing device, operator controlled means including a primary lever, a secondary lever, means whereby movement of the primary lever in one sense of direction compels movement of the secondary lever in one sense only, yieldable means for biasing said primary lever to cause movement of the secondary lever, a link having a lost motion connection from one arm of said secondary lever to an arm of said differential lever, a tensioned spring between the link-connected arms of said difierential lever and said secondary lever, said spring exerting less force than said yieldable means for biasing the primary lever, and arranged so as to exert its elastic force with a greater mechanical advantage on said secondary lever than on the differential lever.

11. In a variable speed transmission mechanism of the class described, a combination as defined in claim 10 with the addition of a yieldable resistor arranged to retard movement of the operator controllable means.

12. In a variable speed transmission mechanism of the kind described, a ratio changing device, a differential lever connectedto said ratio changing device, a movable member to which said differential lever is pivoted, a governor operative on said movable member for changing the position of the pivotal connection between said differential lever and said movable member, a pivoted operator controllable arm, a link connected to the differential lever and said operator controllable arm, a spring joined to said arm and said differential lever at points that enable the spring to operate with a greater mechanical advantage on said arm than on said differential lever, and a yieldable resistor tending to retard the movement of said arm.

13. In a variable speed transmission mechanism of the kind described, a ratio changing device and means for limiting its range of movement, a speed responsive governor, and mechanical connections between the governor and ratio changing device including cushioning means.

I 14. In a. variable speed transmission mechanism of the kind described, a ratio changing device, a differential member connected to the ratio changing device, a speed responsive governor connected to the differential member and exerting a force tending to shift the ratio changing device toward high speed ratio in response to in- I creasing governor speed and toward low-speed ratio in response to decreasing governor speed, and an operator controllable spring connected to said differential member, said spring being stressed to exert its elastic force upon the differential member with a tendency to adjust the ratio changing device toward low-speed ratio position.

15. In a variable speed transmission mechanism of the kind described, a ratio changing .device, a differential member having one end connected to the ratio changing device, a speed responsive governor operative on the differential member between its ends, an operator movable member, a link having a lost motion connection to said operator movable member and to the other end of said differential member, and a takeup and power spring tending by exerting its elastic force to shorten the distance between said members, said spring being joined to said members at points removed from the link connections thereto.

HENRY J. KIRSCHNER. WINFIELD D. GOVE. 

